DE102011052266A1 - Self-locking fasteners and mounting arrangement - Google Patents

Abstract

The invention relates to a self-locking fastening means for interacting with an external thread (25) in order to exert a clamping force on a component (27) to be secured. According to the invention it is provided that the screw nut (2) or the optional cam disk has at least one first tightening stop surface (17) effective in the tightening direction (F) for interaction with a second tightening stop surface (18) of the ring element (10), so that the screw nut (2 ) or the optional cam disk (33) the ring element (10) when force is applied to the drive (7) of the screw nut (2) with the tool in the tightening direction (F) in the tightening direction (F), in particular after the first cam surface (15 ) along the second cam surface (16), and that the braking means (3) are designed and constructed in such a way that they prevent the screw nut (2) from rotating when the ring element (10) is rotated counter to the tightening direction (F) when force acts on the ring element (10) against the tightening circumferential direction, an axial relative adjustment movement between the screw nut (2) and the ring Gelement (10) to cause away from each other in order to thereby tighten the nut (2) and the ring element (10) against each other.

Description

The invention relates to self-locking fastener according to the preamble of claim 1 for interacting with an external thread to exert on a component to be secured a clamping force or to secure the component against loss. Furthermore, the invention relates to a fastening arrangement with such fastening means according to claim 17. Furthermore, the invention relates to a method for securing a component to be secured according to claim 18.

To secure hubs on a journal of a motor vehicle against unintentional loosening it is known to unscrew when plugged hub on the external thread of the journal nut and this form-fitting after tightening rotatably connected to the journal by the force of the nut from radially outside to radially inside is formed and thereby in corresponding radially inwardly projecting protrusions in the axial end portion of the axle journal. The fastening method is therefore relatively complex and requires a variety of operations and tools. In addition, a loosening of the nut due to the positive connection to the journal, for example, for repair or replacement purposes only very expensive possible.

In principle, self-locking fastening means for exerting a clamping force on a component to be secured (but not in connection with wheel hubs) are known which comprise, in addition to a, first arranged on a lower face cam surfaces having a ring nut, which on one of the nut facing upper end side second cam surfaces to cooperate with the first cam surfaces of the nut. Such self-locking fasteners are for example in the EP 1 255 051 A1 , of the EP 088 925 B1 , of the EP 0 350 711 B1 , of the US 5,203,656 , of the US 5,626,449 , of the US 6,554,552 B2 , of the US 5,409,338 , of the US 6,039,524 as well as the US 5,688,091 described. All known self-locking fasteners is common that the cams designed as ramps, contrary to the tightening of the nut, ie viewed in a release direction of the nut in the axial screwing, in which the nut is tighten when tightening on the component to be secured, so that the nut is displaced axially away from the ring member upon application of force in the loosening direction by cooperation of the intermeshing cam surfaces. So that the known fastening means can be loosened again by means of a tool, a drive in the form of wrench flats for cooperation with a tool, in particular a wrench, is provided both on the screw nut and on the ring element.

Securing the wheel hub to the journal by means of fasteners described above has proved to be unsafe in non-public trials. It has been observed in internal tests that the self-locking fasteners in the test stand separate from the journal external thread.

From the WO 02/097283 A2 is known a locking nut, which has several, each acting separately securing means. With a first securing means in the form of an axial annular extension, the lock nut is supported on a ring element, whereby the lock nut according to the teaching of WO 02/097283 A2 is pressed axially against the downward flanks of an external thread passing through it. As an additional securing means ring collar-shaped spring means are provided which enhance this Axialverspannung. A further securing means are provided on the nut arranged cams, wherein the cams rise in the tightening direction of the nut viewed against the axial screwing. In this respect, the cams of the nut shown differ from the aforementioned prior art. As is clear from the description of WO 02/097283 A2 yields, the cams are designed such that they slide over the counter-cams of the ring member during tightening, whereby axial shocks are effected. The cams are therefore referred to in the document as a striking cam, which serve to produce thereby microscopically recognizable indentations in a workpiece arranged thereunder, with the aim of increasing the friction between the ring element and the workpiece. As a further separate securing means braking torque means are described, which develop by plastic deformation of a special thread effect. The braking torque means described can only generate a comparatively low braking torque. Overall, the illustrated self-locking fasteners are in need of improvement. In particular, a loosening of the nut with a rotation of the ring member against the tightening direction can not be prevented with the fasteners shown.

In addition, the friction between the ring member and the ground is increased in an undue manner when tightening the nut by the ratcheting of the cam, whereby the risk that the ring element in a rotation of the ground in a Loosening direction is taken while loosening the nut.

From the US 2003/007143 A1 Alternative fastening means are known in which the screw nut and ring element cooperate via cam surfaces which, viewed in the tightening direction, rise counter to the axial screwing-in direction. In the embodiment described in the document, however, can not be prevented that the nut is entrained in a twisting of the ring member in the release direction. In addition, the cams rattle unfavorably when fixing the nut on each other, thus increasing the friction or damage the material surfaces.

From the JP 2003/120643 A Another embodiment of fastening means is known, in which a ring element is fixed in a rotationally fixed manner to an external thread part via form-fitting means. When fixing the nut, there is an unfavorable Überratschen the cam surfaces.

From the DE 10 2004 014 301 A1 a wheel bolt is known which serves for fixing a motor vehicle wheel. The wheel bolt does not have cam surfaces and is not suitable for fixing wheel scars on axle journals of motor vehicles.

From the JP 2000027837 A a locking screw is known, which is supported on cam surfaces on a ring member, wherein the cams rise in the axial screwing.

From the JP 60-167226 fasteners are known which have a nut with cam surfaces, wherein the cam surfaces viewed in the tightening direction increase against the axial screwing. The ring element is supported in a disadvantageous manner via friction-increasing prongs on the ground, can thereby be taken in the release direction, whereby a resulting loosening of the mother can not be reliably prevented.

From the DE 60 206 116 T2 fasteners are known in which a ring member is rotatably fixed to an external thread member via positive locking means.

The DE 10 205 300 C1 describes a releasable fastener in the form of a screw having cam surfaces that disadvantageously increase in the tightening direction in the axial screwing direction. The known screw has Festziehanschlagflächenpaare. A loosening of the screw during a rotation of the Gegennockenparts can not be safely avoided.

From the WO 2004/033139 A2 fasteners are known in which a release of the same can not be reliably prevented. The known fastening means operate with cam surfaces which, viewed in the tightening direction, increase in the axial screwing-in direction. In particular, for applications in which the ring element is entrained against the tightening direction due to a corresponding movement of the background, as in the fixing of Radnarben on journals, a release can not be reliably prevented.

The DE 1 625 279 shows fasteners cause a bias on the basis of a cam adjustment, with a backup against automatic release is not secured.

From the FR 415345 are known fastening means which interact via inclined planes.

The EP 2009 158 A1 also shows fastening means for fixing components.

Based on the aforementioned prior art, the present invention seeks to provide self-locking fasteners, which u. a. are suitable for securing hubs to journals of motor vehicles preferably without the need to connect the fasteners form-fitting with the journal. Furthermore, the object is to provide a correspondingly improved fastening arrangement comprising a self-locking fastening means, a wheel hub and a Außengewindeachszapfen. In addition, the object is to provide a simplified method for fixing a wheel hub to a journal of a motor vehicle.

This object is achieved with regard to the self-locking fastening means with the features of claim 1, with regard to the fastening arrangement having the features of claim 17 and with regard to the method having the features of claim 18. Advantageous developments of the invention are specified in the subclaims. All combinations of at least two features disclosed in the description, the claims and / or the figures fall within the scope of the invention.

The inventor has recognized that a cause for releasing known securing elements from the external thread of a journal is that the hub is usually fixed by a play-bearing wedge payment on the journal, and the play a minimum relative movement of the journal and the hub in the circumferential direction allows. In the occurring in operation in the circumferential directions changing loads this leads to that in known self-locking Fastening the ring member is taken from the wheel hub in a release direction, whereby the bias between the nut and ring element is reduced or even released, which in turn loses the security function and the securing means can detach from the journal. The invention has further recognized that the (pressure) loss of tension between ring element and nut is due to the fact that in the known self-locking fasteners, the interacting cam surfaces of the nut and the ring element in the tightening direction fall in the axial screwing, whereby the nut and to move the ring member towards each other in the above-explained case. To remedy the vorgenanten disadvantages or the problem described, the invention proposes to modify the self-locking fastener such that the at least one first cam surface and / or the at least one second cam surface are inclined in the opposite axial direction, such as in the EP 1 255 051 A1 shown cam surfaces, so that screw nut and ring element axially displaced away from each other when force applied to the ring element in the release direction of the nut and thus biased more. In other words, the invention proposes to let the at least one first cam surface and / or the at least one second cam surface in the tightening direction rise counter to the axial screwing-in direction, ie that the pitch of the first and / or second cam surface opposes the internal thread pitch of the internal thread of the nut is.

If, in the case of the self-locking fastening means according to the invention, the component to be secured, in particular the wheel hub, carries the ring element somewhat counter to the tightening direction, this will cause the second cam surface to move counter to the tightening direction, ie. H. is displaced in a release direction and thereby the nut is pressed against the axial screwing, which in turn the bias between the nut and ring element is increased, which then brings the self-locking effect with it. The tightening torque of the self-locking fastener according to the invention increases almost automatically. The first and second cam surfaces are thus formed so that they cooperate so that they axially spaced from one another and thereby clamp the nut and the ring member upon application of force of the ring member against the tightening direction. The fastening means formed according to the concept of the invention are therefore suitable for the first time for fastening arrangements in which there is a tendency for the ring element to be subjected to a force in the release direction.

The circumferential extent of the first and the second cam surface should be coordinated so that a relative displacement of the nut and ring member over a peripheral portion is possible to allow the biasing.

According to the invention that the threaded connection of the nut and external thread, preferably formed on the nut braking torque are assigned, which are further dimensioned according to the invention so that they increase the friction between the nut and the external threads such that the nut is stationary, ie that a Rotation of the nut is prevented when the ring member is rotated due to a corresponding movement, in particular pivotal or rotational movement of the substrate against the tightening direction, thereby ensuring a sliding of the first and second cams, ie a Relativverdrehbewegung the cam to thereby again an axial Relativverstellbewegung To cause or guarantee between the nut and ring element, in order to tighten in turn stronger axially against each other nut and ring member against each other and thus to prevent an automatic release. The invention thus has contrary to the teaching of WO 02/097283 A2 recognized that it is not simply sufficient in addition to obliquely extending cam so to speak as another or alternative securing means to provide braking torque, but that it is necessary to dimension these braking torque means such or vote on the friction between the first and second cam that the nut at a twisting movement of the ring element stops against the tightening direction. Only hereby only a stronger tightening of the nut relative to the ring element and thus a safeguard against an automatic release is reliably prevented. As will be explained later, is provided in a further development of the invention to form the braking torque means such that these, the braking torque, preferably exclusively, by elastic deformation of a portion of the braking torque effect, as for example by the in the WO 2007/076968 A1 known braking torque can be achieved. The in the WO 02/097283 A2 shown braking means work entirely due to a plastic, ie non-reversible deformation and are not designed to apply the required braking torque. This is preferably for wheel mounting applications more than 25 Nm, preferably more than 30 Nm, most preferably between about 31 Nm and about 80 Nm or more, preferably between 31 Nm and 50 Nm.

If the braking means are designed so that they can generate the braking torque exclusively by elastic deformation of a portion of the braking torque means at least one of the cooperating thread, so in the case of the arrangement of the braking torque means on the nut the external thread advantageously as a standard thread, in particular as a metric standard thread or as Customs threaded be ausgebldldetet. The use of special threads such as a Sägezahngewindes can be omitted with advantage.

Optimal securing results can be achieved in that the nut is not a conventional nut, but a nut with braking torque, which cause a braking torque when screwing and / or loosening, in particular by interaction with the external thread, the braking torque screwing or solving difficult. For this purpose, for example, two axially adjacent internal thread sections may be arranged offset from one another in the axial direction and / or in the circumferential direction in such a way that the desired torque results. It is also possible, the braking torque as in the WO 2007/076968 A1 described by the applicant. There, an annular collar is integrally formed on one of the end faces of the nut and bent crosswise as achsähts that it limits a female thread opening as a support surface surrounding portion of each end face of a directly associated receiving slot. According to the invention, the braking means are designed and dimensioned in such a way that the friction force between the at least one first cam surface and the at least one second cam surface is insufficient to entrain the nut against the tightening direction when the rotational movement of the ring element against the tightening direction is initiated. but that preferably the nut remains stationary, while the ring member is adjusted against the tightening direction and thereby due to the sliding of the cam surface, the bias between the nut and the ring member is increased.

According to the teaching of the invention, it is additionally necessary for achieving an optimal self-locking function of the first cam surface an effective Festziehrichtung first Festganganschlagsfläche which cooperates when tightening the nut with a provided on the ring element second Festziehanschlagfläche. In other words, at least one Festziehanschlagflächenpaar is provided for tightening or securing securing the fastening means, in particular of the ring element, which is preferably located on a laterally to be explained Löseanschlagflächenpaar in the tightening direction end of a pair of cam surfaces. The tightening abutment surface pair includes a first tightening abutment surface of the nut or alternatively an optional cam for co-operating with a second tightening abutment surface of the ring member, the first tightening abutment surface being preferably disposed opposite to the tightening direction adjacent to the second tightening abutment surface such that the first tightening abutment surface upon rotation of the nut in the tightening direction Tool the second Festziehanschlagfläche and thus the ring member in the tightening direction, especially after overcoming the cam surface slopes, can take. It is very particularly preferred if the tightening stop surface pair is aligned and arranged parallel to a release stop surface pair and spaced apart in the tightening direction.

Such tightening stop surfaces are in the WO 02/0997283 A2 not provided or contradict even the teaching there, since in the known from the aforementioned document fastening the cam surfaces serve to ratchet when tightening each other, thereby causing an increase and decrease in torque, run with the aim of axial shocks to to increase the friction between ring element and ground. The cams are therefore referred to in the aforementioned document as so-called impact cams (bump-cams). The aim is to drive in microscopically visible depressions in the workpiece, thereby increasing the friction bond. Just this is to be prevented according to the invention, by the provision of the tightening stop surfaces. The friction between ring element and ground should be as minimal as possible. In addition, only allow the Festziehanschlagflächen that later still to be explained fastening or securing method, after which the nut is first screwed to reach a first tightening torque and then twisted back, wherein when tightening the Festziehanschlagflächen a Festziehanschlagpaares abut each other.

In summary, the invention has recognized that a variety of features not only realized but also matched to each other, so that the self-locking fasteners reliably fulfill their self-locking function. Thus, to prevent over-ratcheting of the camming surfaces, it is necessary to provide at least one tightening stop surface pair which cooperates in tightening the nut to thereby rotate the ring element. In addition, it is essential that the brake fluid, which are preferably formed on the nut, and which preferably act exclusively by elastic deformation, ie are reversibly deformable, are designed so that a sufficiently large braking torque is generated, which reliably prevents the nut is mittwreht when the ring member against the tightening direction, ie moved in the release direction. Only this way it can be ensured that ring element and nut are braced against each other axially stronger, so that only the security function is reliably fulfilled.

In a further development of the invention is advantageously provided that the nut exclusively on cam surfaces, ie, for example, not one in the WO 02/097283 A2 described support ring or extension is supported on the ring member. In the case of the provision of the cam disc, this is supported exclusively on cam surfaces on the ring element. In other words, the axial clamping of the nut and ring element in the fixed state is achieved exclusively by the interaction of cam surfaces. A theoretically possible embodiment in which as in WO 02/097283 A2 described, an additional support over another support surface (not a cam surface, such as a ring collar) is realized, the desired backup function is detrimental.

It is particularly preferred if the first cam surface and / or the second cam surface are formed as a ramp with a pitch angle / is greater than the internal thread pitch angle of the internal thread of the nut. Preferably, the pitch angle of at least one of the cam surfaces, preferably each of the cam surfaces of the at least one cam surface pair is between 1.5 to 6 times, preferably between 2 to 5 times, more preferably between 3 to 4 times that inside pitch angle. As already indicated, it is preferred if the pitch of the cam surfaces of a pair of cam surfaces and, in the case of several pairs of cam surfaces, preferably equal to each pair of cam surfaces. Due to the larger pitch angle ensures that when moving the ring member in the release direction, the axial clamping force is increased.

Preferably, the ring element used is a disc which is provided with an annular bearing surface on the side remote from the nut, said bearing surface preferably extending in a radial plane which is oriented perpendicular to the screwing.

If the pitch angle were chosen too large, this may result in the cam surfaces acting as release stop surfaces, which could result in detachment of the fasteners.

In a further development of the invention is advantageously provided that a tool drive for releasing the fastening means is provided exclusively on the nut and no other component of the fastening means, in particular not on the ring member and / or later to be explained, optional securing means for captive holding the ring element on the nut. In other words, the fastening means can be released by exclusive cooperation of a tool with the nut.

In order to be able to loosen the fastening means, in particular without the need for a drive for interacting with a tool on the ring element comfortable, is provided in a further development of the invention advantageously that the nut has at least a first Löseanschlagsfläche, which is designed to cooperate with a second Löseanschlagfläche the ring element and arranged. The first release stop surface of the Löseanschlagflächenpaares is located in the tightening direction adjacent to the second Löseanschlagfläche and takes the second Löseanschlagfläche against the tightening with when pressed against the tightening direction when loosening the nut against the second release stop surface of the ring member. In order for the first release stop surface to abut the second release stop surface, the cam surfaces of the cam surface pair must first be adjusted correspondingly relative to one another, preferably in such a way that the nut and the ring element take up the minimum possible axial distance from one another.

It is preferred if the first release stop surface and / or the second release stop surface have a greater pitch than the slope of the first and second cam surfaces. It is preferred if the first release stop face and / or the second stop stop face are oriented perpendicular to the circumferential direction of the nut, that the first and / or second release stop face thus span a plane extending in the radial direction and in the axial direction.

It is particularly useful if the first Festziehanschlagfläche and / or the second Festziehanschlagfläche have a greater slope than the slope of the first and second cam surface, or that the first Festziehanschlagfläche and / or the second Festziehanschlagfläche, at least approximately, aligned parallel to the axial screwing are / is, so spanning / spanning a plane extending in the axial and in the radial direction. It is particularly expedient if a plurality of circumferentially spaced first pinnacles are provided on the nut and second pinnacles spaced on the ring element in the circumferential direction over the first pinnacles, the first and second pinnacles preferably engaging one another in the axial direction in the manner of a toothing. Preferably, at least one of the first pinnacles both a first Festziehanschlagfläche for cooperation with a second Festziehanschlagfläche is provided, which is arranged on a second Zinnen in the tightening direction of the ring element, as well as a first Löseanschlagfläche for cooperation with a second Löseanschlagfläche another, against the Clamping direction adjacent second ring of the ring element.

Preferably, the distance between the first Festziehanschlagfläche and a first Löseanschlagfläche a pair of cam surfaces is larger or smaller, for example, greater than the distance of a second Festziehanschlagsfläche and a second Löseanschlagsfläche this pair of cam surfaces, so as to allow a relative Verdrehbarkeit and thus a bracing. It is preferable to ensure that the first and second tightening abutment surfaces of a pair of abutment surfaces in the tightening position are spaced from each other.

In principle, it is possible for first or second cam surfaces to be provided either only on the lower end faces of the first pinnacles or only on the upper end faces of the second pinnacles, and the counter cam surfaces in each case in the peg intervals or depressions of the opposing component. According to an alternative embodiment, located on the lower end faces of the first pinned first cam surfaces, the second cam surfaces of the ring element contact and at the same time located on the upper end faces of the second battles second cam surfaces which cooperate with first cam surfaces of the nut.

In principle, it is possible to handle the ring element and the nut as separate components. However, the installation or the backup process can be much easier and error-free designed when the ring member is arranged captive on the nut. This can for example be realized in that the ring element rests with its remote from the nut (lower) side on a locking ring which secures the ring element captive on the nut and which is arranged relatively rotatable both to the nut and to the ring member. Alternatively, it is conceivable to secure the ring element by direct positive engagement with the nut, and here too attention must be paid to an at least partial relative rotatability between the nut and ring element. In the case of providing an optional cam can this be secured by means of the locking ring or the ring member between the ring member and nut.

It is particularly useful in the case of providing a retaining ring when the friction between the ring member and the locking ring and / or between the locking ring and the component to be secured, in particular the hub is reduced, in particular with the aim of the least possible force or To ensure torque effect of the component to be secured on the ring element. This can be realized, for example, in that the securing ring has a friction-reduced underside facing the component to be secured and / or a friction-reduced upper side facing the ring element. The reduction in friction can be achieved, for example, by the provision of a friction-reducing, single- or double-sided coating. Additionally or alternatively, the securing ring may be a hardened component, which is characterized by a reduced static friction. Most preferably, the stiction of the circlip by nitriding, d. H. Nitrogen enrichment reduced.

Very particular preference is given to a variant embodiment in which the at least one first cam surface and the at least one second cam surface are formed as a ball and socket pair, ie cooperate in the manner of a ball and socket joint, so that the nut can be pivoted relative to the ring element is, on a surface portion of an imaginary spherical surface (Kalottenoberfläche), ie around the center of the ball surface having this sphere. Very particular preference is given to an embodiment with a plurality of first cam surfaces and a plurality of second cam surfaces corresponding to the first cam surfaces, wherein it is even more preferred if the first cam surfaces and the second cam surfaces are distributed uniformly in the circumferential direction. Due to the articulated pivotability between the first and the second cam surfaces tolerances, especially runout errors in the assembly of the fastening means can be compensated automatically. In other words, self-centering is achieved by the surface contouring according to the invention of the first and second cam surfaces or the nut is aligned axially, so that a longitudinal center axis of the nut with the longitudinal central axis of the Nut screwed male thread element coincides.

The aforementioned ball and socket pairing can be achieved in two different ways. According to a first alternative, the first cam surfaces are convex, d. H. contoured spherical segment and the second cam surfaces corresponding concave, d. H. pan-like. According to a second alternative, the first cam surfaces are contoured in the manner of a cup section and the second cam surfaces are shaped in the shape of a spherical segment.

In other words, the invention provides for the screw nut to be arranged or formed pivotable about an imaginary center point relative to the ring element, which is achieved in that the first cam surfaces are formed as surface sections of a common convex spherical envelope contour and the second cam surfaces as surface sections of a common cam surface concave pan contour corresponding to Kugelhüllkontur, or vice versa, d. H. the first cam surfaces are formed as surface sections of a common concave socket envelope contour, and the second cam surfaces as surface sections of a common convex ball envelope contour corresponding to the socket envelope contour.

In this case, it is advantageously provided that the radius of the ball envelope contour and the radius of the corresponding pan envelope contour correspond - in other words, the radius of the ball envelope contour with respect to a common center corresponds to the radius of the pan envelope contour with respect to this center point.

The invention also relates to a fastening arrangement with fastening means designed according to the concept of the invention. The fastening arrangement comprises a journal of a motor vehicle, wherein an external thread for screwing to the nut of the fastening means is provided on the axle journal. As a component to be secured, a wheel hub is provided, which is fixed to the axle journal, in particular such that the connection is play-related in the circumferential direction. For this purpose, for example, a spline can be used. By trained according to the concept of the invention, self-locking fasteners unintentional release of the plugged onto the journal hub is not possible because in the case of Relativverstellbewegung the hub together with the ring member against the tightening of the nut due to the inventive pitch arrangement of the cam surfaces an increased voltage between the nut and ring element and thus an increased pressure of the ring element in the direction of the wheel hub results, whereby it is secured or the connection is reinforced. A positive connection between the fastening means and the journal as anti-rotation is not necessary and preferably not provided.

The invention also leads to a method for securing a component to be secured, in particular for producing a fastening arrangement described above. For this purpose, the fasteners formed according to the concept of the invention are screwed onto an external thread, preferably onto an external thread of a journal of a motor vehicle, while being twisted in a tightening direction (tightening circumferential direction), whereby the nut in the axial direction, d. H. in the axial screwing on the component to be secured, in particular the hub is moved to. In this case, the screw nut or the optional cam disc takes the ring element over at least one tightening stop surface pair. The twisting in the tightening direction is preferably carried out as long, continuously or in stages, until a first, z. B. maximum, tightening torque is achieved, for example, 330 Nm.

Then, the nut is a little bit far, in particular maximally so far that a first release stop surface of the nut strikes a second Löseanschlagfläche associated therewith without taking the ring member or preferably the second Löseanschlagfläche not yet reached, dissolved, so that the at least one first cam surface a ( small) piece can move along the second cam surface against the tightening direction. As a result, the bias voltage between the screw element and ring element is slightly reduced (preferably not to zero).

After the partial release operation, the nut can be twisted in development of the invention again in the tightening direction continuously or in stages until a second tightening torque is reached, which is greater, preferably significantly greater than the first tightening torque. Preferably, the second tightening torque is at least 10 Nm, preferably 20 Nm, more preferably at least 30 Nm, even more preferably at least 40 Nm larger than the first tightening torque. In particular, the second tightening torque is at least approximately 380 Nm.

Most preferably, the tightening is completed before the first and second Festziehanschlagfläche abut, so that in the tightened state, a distance between them is maintained, whereby the fastening means can bias in Kraftbeaufschlagung the ring member in the release direction itself.

Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings.

These show in:

1 FIG. 2: a sectional view of multipart fasteners along the section line CC according to FIG 2 .

2 a plan view of the fastener according to 1 from above in an axial screwing,

3 : a detail A off 1 .

4 : an oblique perspective view of the fasteners from the outside,

5 : An enlarged view of the fastener according to the 1 to 4 in an outer side view,

6 : An illustration of a fastening arrangement, comprising a stub axle, on which a wheel hub is fixed via a spline, which via the in the 1 to 5 Secured fasteners shown against unintentional release is secured without a Verdrehsicherungsformschluss is realized between the fastening means and the journal,

7a to 7d different views, sections and detailed views of self-locking fasteners comprising a nut and a ring member,

8a and 8b different, partially enlarged sectional views of a screw element,

9a and 9b different views and enlarged detail of a to the nut according to 8a and 8b corresponding ring element,

10a and 10b different, partially enlarged views of the nut according to the 8a and 8b .

11a and 11b different views and detail enlargements of the ring element according to the 9a and 9b , and

12a to 12g different views of fasteners comprising a pair of cam discs.

In the figures, like elements and elements having the same function are denoted by the same reference numerals.

In the 1 to 6 are self-locking fasteners 1 shown. These include a nut 2 with braking torque 3 in the form of two female thread sections 4 . 5 an internal thread 6 , which are axially spaced from each other and resiliently arranged relative to each other, that when screwing the nut 2 with a male thread a braking torque results. With regard to the structure and operation is on the WO 2007/076968 A1 directed.

The nut 2 comprises on its outer periphery designed as a polygonal drive for cooperation with a tool - alternatively configured drives, for example, with parallel key surfaces, etc. are also feasible.

The internal thread 6 limits the inner circumference of a passage opening 8th , which in the axial direction with an insertion opening also designed as a passage opening 9 one of the nuts 2 associated ring element 10 flees. The insertion opening 9 is designed internal thread-free, in any case such that the ring element 10 not in screwing interaction with the internal thread 6 associated external thread can occur.

The ring element 10 is by means of a circlip penetrated by a male thread with radial clearance 11 captive on the nut 2 held. The ring element 10 rests with a base 12 on an upper, annular top 13 of the circlip 11 off, which in the mood state with its bottom 14 preferably supported on the component to be secured. In an alternative embodiment, not shown, either the ring element 10 at the same time designed as a locking ring and form-fitting for axial securing with the nut 2 be connected. Further alternatively, securing means for axially securing the ring element 10 on the screw element 2 , ie completely omitted for captive holding.

As is apparent from the detailed representation according to 3 shows, points the nut 2 at a lower, the ring element 10 facing first side, circumferentially spaced from each other, designed as inclined ramps cam surfaces 15 on, each with a second cam surface 16 of the ring element 10 interact. It can be seen that the first and second cam surfaces 15 . 16 have the same slope. The cam surfaces 15 . 16 go up in the Festziehrichtung F considered against the axial screwing E on, so extend in the tightening direction obliquely against the screwing E, so that the ring element 10 and the nut 2 with fixed fasteners 11 when the ring member is urged against the tightening direction F, move in the circumferential direction relative to each other, such that nut 2 and ring element 10 be stronger against each other.

The slopes of the first and second cam surfaces 15 . 16 are here of the pitch direction of the inner thread pitch of the internal thread 6 opposed. In addition, the slope of the cam surfaces 15 . 16 preferably three to four times greater than the internal thread pitch of the internal thread 6 the nut 2 ,

Each of a first and a second cam surface 15 . 16 existing cam surface pair (at least, however, a pair of cam surfaces) is associated with a tightening stop surface pair, comprising a first, the screw nut side first tightening stop surface 17 , which preferably the first cam surface assigned to it 15 limited against the tightening direction F. The first tightening stop surface 17 is in Festziehrichtung F against a second Festziehanschlagfläche 18 that the first tightening stop surface 17 while tightening the nut 2 by means of one with the single drive 7 cooperating tool in the tightening direction F can take after the first cam surface 15 as far along the associated second cam surface 16 was twisted in the circumferential direction until first and second tightening stop surfaces 17 . 18 abut each other or abut against each other, in which state the nut 2 and the ring element 10 (sections) are at most far axially spaced apart. In the embodiment shown, the tightening stop surfaces extend 17 . 18 in the axial and in the radial direction.

Furthermore, it can be seen that, in the exemplary embodiment shown, each cam surface pair, preferably at least one of the cam surface pairs, is assigned a release stop surface pair, comprising a first release stop surface on the screw nut side 19 and one of these opposite the tightening direction F opposite, the ring element side second Löseanschlagfläche 20 ,

The release stop surfaces 19 . 20 are parallel to the tightening stop surfaces 17 . 18 aligned and limit in Festziehreichtung the first and second cam surface 15 . 16 , In the in 3 shown relative position, in which the first Löseanschlagfläche 19 at the second release stop surface 20 is applied, the nut can 2 , more precisely the first release stop surface 19 the ring element 10 , more precisely the second release stop surface assigned to it 20 take it against the tightening direction F.

Out 3 it also follows that on the nut first, towards the ring element 10 extending battlements 21 and on the ring element 10 second battlements 22 are arranged, wherein the second pinnacles 22 in the distances between the first battlements 21 engage in the axial direction like a tooth. The first battlements 21 have in the embodiment shown no first cam surfaces, as well as the first battlements 21 associated peripheral sections between two second pinnacles 22 no second cam surfaces. The second battlements 22 Carry the front side, the second cam surfaces 16 that with the first cam surfaces 15 cooperate in the peripheral sections between two first pinnacles 21 on the nut 2 are formed. A reverse configuration with cam surfaces free second battlements and cams having first pinnacles is alternatively feasible.

Based on 5 Below is the operation of the special configuration of fasteners 1 explained again in detail. You can see the nut 2 with its circumferential drive 7 for a tool and provided on the lower end face first cam surfaces 15 that in second cam surfaces 16 a ring element 10 intervene, ie interact with it. Quite essential is that the first and / or second cam surfaces 15 . 16 , here both types of cam surfaces 15 . 16 in the tightening direction F viewed against the axial screwing E in the nut 2 is moved when tightening in the direction of securing component, and preferably increase with a slope which is greater than that, preferably opposite pitch of the internal thread of the nut 2 ,

It can be seen that the nut 2 a circumferential groove 23 in which the retaining ring 11 (see. 1 ) can engage positively in the radial direction to secure it against axial loss - alternatively, for example, the ring element 10 in the circumferential groove 23 be formed engaging. Other axial securing means are alternatively feasible, if desired.

Out 5 it can be seen that the first battlements 21 in the distances between circumferentially adjacent, second cam surfaces 16 bearing pinnacles 22 intervention. Every first pinnacle 21 (Preferably, however, at least one of the first pinnacles 21 ) has both a first tightening stop surface 17 as well as a counter to the tightening direction F spaced first Löseanschlagfläche 19 on. The first tightening stop surface 17 this is preferred at least a first pinnacle 21 (Which in an alternative embodiment also has a first cam surface 15 can bear) acts together with a spaced in Festziehrichtung F second Festanganschlagfläche 18 a (first) cam surface pair and the first release stop surface 19 acts together with a counter to the tightening direction F adjacent second Löseanschlagfläche 20 a (second) cam surface pair, which in about the first pinnacle 21 spaced apart from the tightening direction F by the first cam surface pair.

Will the ring element 10 in the fixed state of the fasteners 11 , For example, directly through the component to be secured or, for example indirectly via the optional locking ring 11 against the tightening direction F of the nut 2 kraftbeaufschlagt, so wander the second cam surfaces 16 relative to the first cam surfaces 15 contrary to the tightening direction F, which causes the bias between ring element 10 and nut 2 increases, as long as at the time of application of force to the ring element 10 the first tightening stop surfaces 17 from the second tightening stop surfaces 18 are spaced in the circumferential direction. When tightening or fixing the fasteners 1 Care should be taken that this distance is between the at least one first tightening stop surface 17 and its associated second tightening stop surface 18 is maintained or present in the tightened state. For this purpose, the at least one first release stop surface 19 at the assigned at least a second Löseanschlagfläche 20 abutment or something, but preferably not be maximally spaced in the circumferential direction of this. To achieve this, the nut is loosened a little after reaching a first tightening torque and then tightened so far only with a second tightening torque that the first and second tightening stop surfaces (not yet) touch.

The circumferential extent of the first and second cam surfaces 15 . 16 should be coordinated so that a Relativverstellbewegung of nut 2 and ring element 10 over a peripheral portion is possible to allow the biasing.

In 6 is a mounting arrangement 24 shown, the fastening means formed as described above 1 includes. These are with an external thread 25 screwed, which in the illustrated embodiment - but not mandatory - on a journal 26 a motor vehicle is arranged. Here, the external thread acts 25 with the internal thread 6 ie specifically in the embodiment shown with the female threaded sections 4 . 5 together, such that of the braking torque 3 during screwing a braking torque is effected.

The fasteners 1 rely on the optional circlip 11 on the component to be secured 27 , here a wheel hub, off. Alternatively, the ring element is supported 10 without intermediate arrangement of a securing ring 11 to the component to be secured 27 in the axial direction. The component to be secured 27 is, in the embodiment shown via a spline 28 playful rotationally fixed with the journal 26 , more precisely, a lower counter-toothing of the axle journal 26 connected. The fastener 11 is in a fixing position in which a slight relative movement of the ring element 10 to the nut 2 contrary to the locking direction 11 is possible.

Will the ring element 10 , For example, by appropriate displacements or movements during operation of the fastening assembly on the component to be secured 27 , in particular the wheel hub, due to the play-bearing splines 28 slightly something in the circumferential direction is moved back and forth, taken against the tightening direction F, wander the first cam surfaces 15 so relatively along the second cam surfaces 16 that the nut 2 and the ring element 10 are anxious to move away from each other in the axial direction, whereby the bias between the ring element 10 and the nut 2 rises, as the nut is 2 in the axial direction via its internal thread 6 on the external thread 26 supported.

The following is based on the 7a to 11b a particularly preferred embodiment of fasteners 1 described. These are characterized by the fact that the nut 2 and the ring element 10 cooperate in the manner of a ball and socket joint, so that runout errors are automatically compensated or that the nut can align axially with respect to an unillustrated external thread for screwing with the nut during assembly. In the embodiment shown, for reasons of clarity, there is no optional securing ring 11 provided or shown, the ring element 10 captive on the nut 2 holding. In the case of providing such a preferred securing ring this is interpreted to allow a relative pivoting movement of the nut relative to the ring member on the later to be explained, imaginary spherical surface. In the embodiments shown, the nut, more precisely the first cams form a partial surface section or partial surface sections of a ball, ie they are convexly contoured and the second camming surfaces cooperating with the first camming surfaces are concave in the sequence, ie formed as Pfannenabschnittsflächen. Of course, the reverse embodiment is feasible, ie an embodiment in which the pan of the first cam surfaces and the ball or the ball cut of the second cam surfaces is formed.

In 7a are the self-locking fasteners 1 shown in a perspective oblique view. To recognize is a nut 2 with drive 7 and an axially adjacent thereto arranged, drive-free ring element 10 , The nut 2 has a passage opening 8th on, with an insertion opening 9 of the ring element is aligned. On the inner circumference of the nut 2 is an internal thread (internal thread section) 5 formed, whereas the ring element 10 internal thread is free.

The nut 2 acts on frontal first cam surfaces 15 with corresponding second cam surfaces 16 of the ring element 10 in the manner previously described with reference to the preceding embodiments together. In view of the inclination or the pitch direction and arrangement of the cam surfaces 15 . 16 Reference is made to the above embodiments with associated description of the figures.

In 7b is a sectional view along the section line BB according to 7c shown. It can be seen that a contact surface (contact surface) 29 the first and second cam surfaces 15 . 16 on an imaginary sphere surface 30 are arranged, which has a radius R about a center M. This may cause the nut 2 relative to the ring element 10 on this sphere surface 30 align or relative to the ring member 10 pivot.

This becomes particularly clear on the basis of the detail enlargement B according to FIG 7d , There is a section of the sphere surface 30 shown on the nut 2 and ring element 10 relative to each other in the manner of a ball and socket joint are pivotable.

In 7d is a section of a first cam surface 15 shown with a corresponding second cam surface 16 interacts. Evident is the convex shape of the first cam surface 15 the nut 2 and the corresponding concave shape of the associated second cam surface 16 of the ring element 10 , causing nut 2 and ring element 10 , more precisely, the first cam surfaces 15 and the second cam surfaces 16 interact in the manner of a ball and socket joint. In the embodiment shown, the first cam surfaces are formed as surface portions of a common convex Kugelhüllkontur and the second cam surfaces 16 formed as surface portions of a common concave, corresponding to the aforementioned Kugelhüllkontur Pfannenhüllkontur, so that the nut 2 relative to the ring element 10 around the in 7b shown center of the ball envelope contour and the Pfannenhüllkontur are pivotable.

In 8a is the nut 2 shown in a sectional view. The ball contour is marked 31 with its radius R around the center M.

In the 9a and 9b is that to the nut 2 according to the 8a and 8b corresponding ring element 10 shown. It can be seen that the second cam surfaces 16 as surface portions of a Pfannenhüllkontur 32 are formed, which has the same radius R, as the Kugelhüllkontur 31 according to 8a ,

In 10a is the nut 2 shown in an oblique view of the ring member, not shown, facing lower end face. To recognize the first cam surfaces 15 which, viewed in the tightening direction, rise counter to the axial screwing-in direction. This slope is superimposed by the in 10b indicated convex spherical envelope contour 31 which allow cooperation with the second cam surfaces in the manner of a ball and socket joint.

In the 11a and 11b is that to the nut 2 according to the 10a and 10b corresponding ring element 10 with its second cam surfaces 16 shown. To recognize is the in 11b indicated Pfannhüllkontur 32 that with the ball envelope contour 31 the first cam surfaces 15 corresponds.

In the 12a to 12c are alternative fasteners 1 shown in which, in contrast to the preceding embodiments, the first cam surfaces 15 as well as the first tightening stop surfaces 17 and the first release stop surfaces 19 not directly on the nut 2 but at one between nut 2 and the ring element 10 recorded cam 33 are arranged. In other words, the cam plate form 33 and the ring element 10 a pair of cams, with which the nut and the ring element 10 are braced against each other. The mutually facing annular surfaces of nut 2 and cam disk 33 are smooth, so that at least in the non-strained state a relative twisting between nut 2 and the cam surface pair is possible.

The principle of operation in the 12a to 12d shown alternative fasteners 1 basically corresponds to the functional principle of the fastening means explained above, so that in the following essentially the differences between the embodiments will be discussed in order to largely avoid repetitions. With regard to the similarities, reference is made to the above description of the figures and the preceding figures. To better illustrate the interaction of the cam surface pair, consisting of ring element 10 and cam disk 33 will be on the 12e to 12g referenced, this detail of the fasteners according to the 12a to 12d demonstrate.

The self-locking fasteners 1 according to the 12a to 12g serve for fixation in the in the 6 shown way.

The in the 12a to 12d shown nut 2 corresponds in terms of the structure of the braking torque 3 and the internal thread 6 , which is in the insertion opening 9 is the above embodiments. To recognize is a lower smooth ring surface 34 with which the nut is axially on an oppositely directed, ie pointing away from the component to be fastened upper annular surface 35 the cam disk 33 supported, which in turn with their first cam surfaces 15 on opposing second cam surfaces 16 of the ring element 10 supported.

The ring element 10 is sandwiched between the cam plate 33 and an optional circlip 11 , which axially positive fit on the nut 2 is held. For this purpose, the nut engages behind 2 the circlip 11 with a ring process 36 which extends axially along the inner peripheral surfaces of the cam and the ring member and then projects radially outwardly into a radially inner recess 37 (Ring stage) in and with axial distance to the lower, annular bearing surface of the locking ring 11 , In an analogous manner, the cam surface pair, consisting of ring element 10 and cam disk 33 without circlip 11 be secured. In this case, the ring process would be 36 radially in an inner recess, not shown, of the ring element 10 intervention. It would also be possible in the case of waiving the cam 33 either only the ring element 10 or the ring element 10 in combination with the optional circlip 11 on the nut 2 to secure.

In 12g are those on the cam 33 formed, downwardly facing first cam surfaces 15 shown along the larger circumferential extension of the second cam surfaces 16 of the ring element 10 can slide. Out 12g the position of the first tightening abutment surfaces continues 17 the cam disk 33 with, in the embodiment shown, parallel second tightening stop surfaces 18 of the ring element can cooperate.

Likewise, the pairing of first and second Löseanschlagflächen 19 and 20 to recognize.

LIST OF REFERENCE NUMBERS

1

self-locking fasteners

2

nut

3

Braking torque means

4

Internally threaded portion

5

Internally threaded portion

6

inner thread

7

drive

8th

Through opening

9

Through opening

10

ring element

11

circlip

12

bottom

13

top

14

bottom

15

first cam surface

16

second cam surface

17

first tightening stop surface

18

second tightening stop surface

19

first release stop surface

20

second release stop surface

21

first battlements

22

second battlements

23

circumferential groove

24

mounting assembly

25

external thread

26

journal

27

component to be secured

28

spline

29

Contact surface / contact surface

30

spherical surface

31

Kugelhüllkontur

32

Pfannenhüllkontur

33

cam

34

lower ring surface

35

upper ring surface

36

Annular extension

37

recess

F

Tightening direction

e

the screwing

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1255051 A1 [0003, 0020]
• EP 088925 B1 [0003]
• EP 0350711 B1 [0003]
• US 5203656 [0003]
• US 5626449 [0003]
• US 6554552 B2 [0003]
• US 5409338 [0003]
• US 6039524 [0003]
• US 5688091 [0003]
• WO 02/097283 A2 [0005, 0005, 0005, 0023, 0023, 0029, 0029]
• US 2003/007143 A1 [0007]
• JP 2003/120643 A [0008]
• DE 102004014301 A1 [0009]
• JP 2000027837 A [0010]
• JP 60-167226 [0011]
• DE 60206116 T2 [0012]
• DE 10205300 C1 [0013]
• WO 2004/033139 A2 [0014]
• DE 1625279 [0015]
• FR 415345 [0016]
• EP 2009158 A1 [0017]
• WO 2007/076968 A1 [0023, 0025, 0065]
• WO 02/0997283 A2 [0027]

Claims (18)

Self-locking fasteners for interacting with an external thread ( 25 ) to a component to be secured ( 27 ) to exert a clamping force with: • a nut ( 2 ), comprising a passage opening ( 8th ) with internal thread ( 6 ) for screwing with the external thread ( 25 ), a drive ( 7 ) for cooperation with a tool for tightening the nut ( 2 ) in a tightening circumferential direction around the nut in an axial screwing (E) in the direction of the component to be secured ( 27 ), at least one first cam surface ( 15 ), which at a lower end face of the nut ( 2 ) or arranged at a below the lower end face of the nut, one with the passage opening ( 8th ) aligned opening, optional cam disc ( 33 ) is provided, • an axially adjacent to the nut ( 2 ) or the optional cam disc ( 33 ) arranged ring element ( 10 ), one with the passage opening ( 8th ) of the nut aligned insertion opening ( 9 ) for pushing through the external thread ( 25 ) and that at an upper, the nut ( 2 ) facing end face at least one second cam surface ( 16 ), which in the first cam surface ( 15 ) engages around the nut ( 2 ) and the ring element ( 10 ) in a relative rotational movement between the nut ( 2 ) and the ring element ( 10 ) axially relative to each other, wherein the first cam surface ( 15 ) and / or the second cam surface ( 16 ) in the tightening direction (F) increases / increases counter to the axial screwing direction (E), • braking means for increasing the friction between the nut ( 2 ) and the external thread ( 25 ), characterized in that the nut ( 2 ) or the optional cam disc at least one in the tightening direction (F) effective first Festanganschlagfläche ( 17 ) for cooperation with a second tightening stop surface ( 18 ) of the ring element ( 10 ), so that the nut ( 2 ) or the optional cam disc ( 33 ) the ring element ( 10 ) when the power is applied to the drive ( 7 ) of the nut ( 2 ) with the tool in the tightening direction (F) in the tightening direction (F), in particular after a sliding of the first cam surface (FIG. 15 ) along the second cam surface ( 16 ), and, that the braking means ( 3 ) are designed and formed such that this rotation of the nut ( 2 ) with a rotation of the ring element ( 10 ) against the tightening direction (F) in order to prevent the force acting on the ring element ( 10 ) against the tightening circumferential direction an axial Relativverstellbewegung between the nut ( 2 ) and the ring element ( 10 ) away from each other thereby to the nut ( 2 ) and the ring element ( 10 ) stronger against each other. Fastening means according to claim 1, characterized in that the nut ( 2 ) or the optional cam on the ring element ( 10 ) is formed in the axial direction exclusively on at least one cam surface supporting. Fastening means according to one of claims 1 or 2, characterized in that, preferably on the nut ( 2 ) arranged braking torque means the braking torque, preferably exclusively, are formed by causing elastic deformation. Fastening means according to one of claims 1 or 2, characterized in that the pitch angle of the first and the second cam surface ( 15 . 16 ) is equal and / or that the first cam surface ( 15 ) and / or the second cam surface ( 16 ) are designed as a ramp with a pitch angle of 1.5 to 6 times, preferably 2 to 5 times, even more preferably 3 to 4 times the internal thread pitch angle of the internal thread ( 6 ) of the nut ( 2 ) corresponds. Fastening means according to one of the preceding claims, characterized in that the ring element ( 10 ) and / or the optional cam disc is designed drive-free. Fastening means according to one of the preceding claims, characterized in that the nut ( 2 ) at least first release stop surface ( 19 ) for interacting with a counteracting the second tightening (F) effective release surface ( 20 ) of the ring element ( 10 ), so that the nut ( 2 ) the ring element ( 10 ) when the power is applied to the drive ( 7 ) of the nut ( 2 ) with the tool against the tightening direction (F) against the tightening direction (F), in particular after a sliding of the first cam surface ( 15 ) along the second cam surface ( 16 ), takes along. Fastening means according to claim 6, characterized in that the first release stop surface ( 19 ) and / or the second release stop surface ( 20 ) have a greater pitch than the pitch of the first and second cam surfaces (FIG. 15 . 16 ), or that the first release stop surface ( 19 ) and / or the second release stop surface ( 20 ), at least approximately, parallel to the axial screwing (E) are aligned / is. Fastening means according to one of the preceding claims, characterized in that the first fastening stop surface ( 17 ) and / or the second tightening stop surface ( 18 ) have a greater pitch than the pitch of the first and second cam surfaces (FIG. 16 ), or that the first tightening stop surface ( 17 ) and / or the second tightening stop surface ( 18 ), at least approximately, parallel to the axial screwing (E) are aligned / is. Fastening means according to one of claims 6 to 9, characterized in that the first attachment stop surface ( 17 ) over the in the tightening direction (F) rising first cam surface ( 15 ) from the first release stop surface ( 19 ) is spaced and that the second tightening stop surface ( 18 ) over the tightening direction (F) rising second cam surface ( 16 ) from the second release stop surface ( 20 ) is spaced. Fastening means according to one of claims 6 to 10, characterized in that on the nut ( 2 ) or on the optional cam disc ( 33 ) a plurality of circumferentially spaced first battlements ( 21 ) and on the ring element ( 10 ) several in the circumferential direction over the first battlements ( 21 ) spaced second battlements ( 22 ) are provided, and that the first and the second battlements ( 21 . 22 ) engage in a tooth-like manner, and that on at least one of the first pinnacles ( 21 ) both a first tightening stop surface ( 17 ) for cooperation with a second tightening stop surface ( 18 ) is provided, which at a in the tightening direction (F) adjacent the second brow ( 22 ), as well as a first release stop surface ( 19 ) is provided for cooperation with a second release stop surface ( 20 ) a counter to the tightening direction (F) adjacent second batt ( 22 ). Fastening means according to claim 11, characterized in that either lower end faces of the first battlements ( 21 ) or upper end faces of the second battlements ( 22 ) in each relative rotational position between the nut ( 2 ) and the ring element ( 10 ) are spaced from each other, or that at the lower end faces of the first battlements ( 21 ) first cam surfaces ( 15 ) for cooperation with second cam surfaces ( 16 ) and at the upper end sides of the second battlements ( 22 ) second cam surfaces ( 16 ) for cooperation with first cam surfaces ( 15 ) are arranged. Fastening means according to one of the preceding claims, characterized in that the ring element ( 10 ) captive on the nut ( 2 ) is arranged, preferably in that the ring element ( 10 ) with its from the nut ( 2 ) facing away from rests on a retaining ring, the ring element ( 10 ), preferably together with the optional cam disc ( 33 ), captive on the nut ( 2 ) and the relatively rotatable both to the nut ( 2 ) as well as to the ring element ( 10 ), or in that the ring element ( 10 ) immediately securing with the nut ( 2 ) cooperates positively in the axial direction. Fastening means according to claim 13, characterized in that an underside of the securing ring ( 11 ) and / or an upper side of the locking ring ( 11 ), in particular by the provision of a Reibreduzierbeschichtung and / or by hardening and / or by nitriding, is reduced friction / is. Fastening means according to one of the preceding claims, characterized in that the at least one first cam surface ( 15 ) and the at least one second cam surfaces ( 16 ) are formed as a ball and socket pair, so that the nut ( 2 ) and the ring element ( 10 ) on an imaginary spherical surface ( 30 ), in particular to compensate for run-out errors and / or for alignment of the internal thread ( 6 ), relative to each other. Fastening means according to one of the preceding claims, characterized in that, preferably spaced uniformly in the circumferential direction, first cam surfaces ( 15 ) as area sections of a common convex spherical envelope contour ( 31 ) are formed and the, preferably uniformly circumferentially spaced second cam surfaces ( 16 ) as area sections of a common concave, to Kugelhüllkontur ( 31 ) Pfannenhüllkontur correspond ( 32 ), or vice versa, so that the nut ( 2 ) relative to the ring element ( 10 ) is pivotable about an imaginary center (M). Fastening arrangement with fastening means according to one of the preceding claims, characterized in that the external thread ( 25 ) on a journal ( 26 ) of a motor vehicle, and that the component to be secured ( 27 ) is a wheel hub of the motor vehicle, and that the wheel hub, in particular via a spline ( 28 ), on the journal ( 26 ). Backup procedure for securing a component to be secured ( 27 ) using fasteners according to any one of claims 1 to 16, in particular for producing a fastening arrangement according to claim 17 with the steps: • unscrewing the fastening means ( 1 ) on an external thread ( 25 ), preferably a journal ( 26 ) of a motor vehicle, while twisting the Nut ( 2 ) in a tightening direction (F), so that the nut ( 2 ) axially in a screwing direction (E) in the direction of the component to be secured ( 27 ), in particular a wheel hub of a motor vehicle, is adjusted until reaching a first tightening torque, then turning the nut ( 2 ) over a circumferential angle against the tightening direction (F), such that the first cam is moved a distance along the second cam, and thereby reducing the tension between the screw element and ring element (FIG. 10 ). A method according to claim 18, characterized in that after reducing the voltage, the nut ( 2 ) is again rotated in the tightening direction (E) with a second tightening torque that is greater, preferably at least 10 Nm greater than the first tightening torque, so that the voltage between the screw element and ring element ( 10 ) is again increased, preferably not up to a maximum by interaction of the cam surfaces possible value.

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